Compact gas pressure regulator

ABSTRACT

A compact, gas pressure regulator makes use of a substantially disc-shaped member which is biased within the regulator by one or more spring members exerting forces on the disc-shaped member at multiple, discrete locations which are angularly separated from each other about the area of the first surface. Movement of the disc-shaped member toward or away from a high pressure orifice maintains a regulated, lower pressure for delivery through an outlet in the regulator. A member for mounting a pressure gauge is secured to the housing of the pressure regulator without substantially increasing the overall length of the regulator.

FIELD OF THE INVENTION

This invention relates to devices for controlling the pressure of gas,such as oxygen, and more particularly, to a compact gas pressureregulator.

BACKGROUND

Pressure regulators are generally used in conjunction with cylinders orother sources of pressurized gas, such as oxygen. Pressure regulatorsare sometimes used in conjunction with relatively compact cylinderswhich contain gas under relatively high pressure of between about 500and about 3,000 psi. The gas cylinder and pressure regulator connectedthereto form a gas delivery apparatus. Gas pressure regulators find usein a variety of medical applications, such as for emergency treatment,and for hospital and clinical usages. Gas delivery systems are also usedby ambulatory medical patients, in nursing facilities, and in home-careenvironments.

In many medical or commercial applications, the gas or oxygen from suchhigh pressure source is to be delivered at a constant, lower pressureappropriate for the particular application. Gas delivery often must alsobe accomplished at a constant flow rate and, accordingly, gas deliveryapparatus often use flow control valves in conjunction with gas pressureregulators.

Gas pressure regulators used in gas delivery apparatus suffer fromvarious drawbacks and disadvantages. Gas pressure regulators such asthat shown in U.S. Pat. No. 4,655,246 have undesirably lengthy profilesand use an undesirably large amount of material thickness to attain theruggedness required for safe and effective operation. The amount ofmaterial used in these and other pressure regulators contributesunnecessarily to excessive weight.

The disadvantages of excessive weight and an excessively long profileare often amplified when current pressure regulators are used inconjunction with compact, high pressure cylinders. When the pressureregulator is connected to such a compact cylinder, it often extendsbeyond the cross-sectional footprint of the cylinder. This means that ifthe cylinder were to tip over or otherwise come into sudden contact withanother surface, the pressure regulator attached to such cylinder risksbeing struck by an unyielding surface and potentially damaged. Thelength and weight of current pressure regulators may also significantlyraise the center of gravity of such compact gas cylinders, therebymaking them difficult to manipulate and prone to tipping over.

When the gas delivery apparatus needs to be transported, such as inmobile medical applications or with an ambulatory patient, the weight ofthe pressure regulator takes on increased significance and thedisadvantage of excessive weight is amplified further.

Accordingly, there is a need for a gas pressure regulator and anassociated air delivery apparatus free of the drawbacks anddisadvantages outlined above.

There is a further need for the gas pressure regulator to be lightweightyet suitably rugged, compact, and dimensioned so as to avoid inadvertentdamage when used in a variety of applications.

SUMMARY OF THE INVENTION

It is an object of this invention to overcome the shortcomings of theprior art by providing a compact gas pressure regulator which includes ahousing with a chamber therein. The chamber is sealed from theatmospheric pressure outside the housing. An orifice is located in thehousing for receiving gas from a source, and an outlet is also providedin the housing through which gas is delivered at a delivery pressurewhich is lower than the pressure of the source. Within the chamber is asubstantially disc-shaped member which has a center and two, oppositesurfaces. One of the surfaces includes a seat having a first surfacearea which faces the orifice; the other surface has a second surfacearea larger than the first surface area and forms a head region inconjunction with one of the walls of the chamber. The head region is inpneumatic communication with the gas outlet. One or more spring membersare positioned within the chamber to be biased against the disc-shapedmember. The spring member or members exert forces against thedisc-shaped member at locations which are angularly spaced about thearea of the disc-shaped member. When pressurized gas is present in apressurized zone of the chamber, the disc-shaped member and the seat aremoved toward the orifice and against the bias of the springs to regulatethe delivery pressure.

In one version of the invention, there are multiple spring members whichare helical springs with longitudinal spring axes. The housing isgenerally cylindrical and has a predetermined length. A mounting memberfor a pressure gauge is located on the housing in such a way to avoidsubstantially increasing the predetermined length of the cylindricalhousing.

According to another aspect of the invention, there are four springsspaced symmetrically about the first surface of the disc-shaped member.Pins extend from a transverse inner wall of the housing and receive thesprings thereon. The springs extend between the transverse inner walland the disc-shaped member. The springs are selected to resist movementof the seat toward the orifice in sufficient amount to maintain thedelivery pressure under 100 psi.

In another version of the invention, there is a single spring membercomprising a spring washer, also known as a wave washer. The peaks andvalleys of the spring washer exert angularly spaced forces against thedisc-shaped member.

BRIEF DESCRIPTION OF THE DRAWINGS

There is shown in the drawings an exemplary embodiment of the inventionas presently preferred. It should be understood that the invention isnot limited to the embodiment disclosed and is capable of variationwithin the scope of the appended claims.

In the drawings,

FIG. 1 is a perspective view of a gas pressure regulator incorporatingthe principles of the present invention;

FIG. 2 is a side, sectional view of the regulator of FIG. 1;

FIG. 3 is a side, sectional view showing the pressure regulator duringits operation;

FIGS. 4, 5 and 6 are top plan, side sectional, and bottom plan views,respectively, of the disc-shaped member of the present invention;

FIG. 7 is an exploded, perspective view of the regulator shown in FIGS.1-6; and

FIG. 8 is an exploded, perspective view of an alternative embodiment ofthe present invention.

DETAILED DESCRIPTION OF THE INVENTION

Referring now to the drawings, and in particular to FIGS. 1 and 7, a gaspressure regulator 21 is shown having a housing 23 and a substantially,U-shaped yoke or bracket 25 extending from the end of housing 23. Yoke25 has a pair of substantially parallel arms 75 which in part define anaperture 27 into which a source of pressurized gas, such as a cylinder(not shown), may be received. A T-clamp 29 is threadably receivedthrough a bore in the end of the yoke 25 and is used to secure the gascylinder or other pressurized gas source to the pressure regulator 21.An orifice 31 extends through the housing as explained in more detailbelow and has one of its openings in communication with the aperture 27of the yoke 25. In this way, orifice 31 may be hooked up to the gascylinder to receive gas at a source pressure.

Referring to FIG. 2, a chamber 39 is formed within housing 23. Ingeneral terms, gas passes through orifice 31, through a pressurized zoneof chamber 39, and is delivered through outlet 32 at a regulated,delivery pressure lower than the source pressure.

Referring now to FIGS. 2 and 5, a substantially disc-shaped member 33 ismovably mounted within the housing 23. A spring means, here shown asmultiple, springs 41, is biased against disc-shaped member 33 atlocations which are radially spaced from center 99 of disc-shaped member33. Springs 41 exert force on disc-shaped member 33 at multiple,discrete locations which are angularly separated from each other aboutthe area of the surface of disc-shaped member 33. In this embodiment,then, each spring 41 is angularly separated from an adjacent one of thesprings 41 by an angle of about 90°. Accordingly, spring force isexerted at four, discrete locations on disc-shaped member 33 separatedby about an angle of 90°. Thus, when the forces are described as beingexerted at discrete, angularly separated locations, this means thatthere is a distance between adjacent force locations, and this distanceis an arc length on the surface of the disc-shaped member 33. In otherwords, if a first ray were to be imagined from center 99 to the locationof one of the forces, the other force locations could be located bycorresponding rays which form an angle with the first ray.

The substantially planar shape of disc-shaped member 33 and angularlyseparated springs 41 permits the axial length of housing 23, includingchamber 39, to be relatively compact, an important feature of thepresent invention.

Another feature of the present invention is a member 43 for mounting apressure gauge 45 (FIG. 2) on housing 23 and in communication withorifice 31. Mounting member 43 is, in this embodiment, block-shaped,integral with housing 23, and is positioned without substantiallyincreasing the overall length of housing 23, thereby reducing the amountof material needed for an operative gas pressure regulator.

Referring now to FIGS. 1, 2, and 7 orifice assembly 47 comprises a boreor orifice 31 extending longitudinally between chamber 39 and aperture27 formed by yoke 25, and having progressively decreasingcross-sectional diameters 51-55. Orifice 31 terminates within chamber 39at a terminal opening 125. Chamber 39 is partly defined bylongitudinally spaced, inner walls 65, 67, which extend transversely atthe ends of the chamber 39. Terminal opening 125 is located intransverse inner wall 65. A pair of mounting studs 57 proximate to theorifice 31 and extending from the outside of housing 23 into aperture27. Mounting studs 57 are used for correctly positioning thehigh-pressure gas source to be connected to regulator 21.

Pressure regulator 21 is generally cylindrical, and housing 23 andchamber 39 are coaxially aligned with respect to each other along alongitudinal, central axis of symmetry 111. The housing 23 thus has agenerally circular, cross-sectional footprint indicated by arrows 59.Mounting member 43 extends outwardly from footprint 59 withoutsubstantially increasing the length of housing 23. A passageway 61communicates between bore 63 in mounting member 43 and orifice 31. Inthis way, pressure gauge 45 may be used to read the source pressureentering orifice 31.

Although mounting member 63 may assume a variety of overall shapes, inthis embodiment the member 43 comprises a block having a side 69 whichextends outwardly from housing 23 in a direction transverse to thelongitudinal axis 111 of regulator 21, and in a plane which issubstantially coplaner with that containing the inner chamber wall 65.The block further comprises longitudinal sides 71 which likewise extendoutwardly from housing 23 and thus beyond the circular footprint 59 ofregulator 21. The longitudinal sides 71 extend longitudinally from thetransverse side 69 to terminate at another transverse side 73 ofmounting member 43. Transverse side 73 extends outwardly from thecircular footprint 59 near the end of one of arms 75 of yoke 25.

The above-described structure of mounting member 43 is suitably rigid toreadily receive pressure gauge 45 within bore 63 while advantageouslyusing a minimum amount of material and without substantially increasingthe overall length required for the regulator 21 to function asintended. Referring now to FIG. 3, the outwardly extending sides 69, 71and 73 allow bore 63 to have a bottom 64 (FIG. 3) positioned radialdistance 66 (FIG. 3) from the inner surface of yoke arm 26. Absentsufficient outward extension of sides 69, 71, and 73, material toreceive the bore 63 would need to be added between the transverse wall65 of chamber 39 and opposite wall 68 of aperture 27 in order tooperably define and accommodate the bore 63. Such additional materialwould undesirably increase the length and weight of the regulator 21.

Referring now especially to FIGS. 2-3, disc-shaped member 33 is axiallymovable within chamber 39, that it, disc-shaped member 33 is mountedwithin chamber 39 and capable of movement in a direction generallycorresponding to the orientation of longitudinal axis 111 of regulator21. Disc-shaped member 33 has a center 99 substantially aligned with thelongitudinal axis 111, a surface 77 which generally opposes or facesorifice 31, and a surface 79 opposite the surface 77. The surface 79generally opposes the inner wall 67 of chamber 39 and defines a headregion 81 which is in communication with the outlet 32 through which gasof regulated pressure is delivered.

Referring also to FIGS. 4-6, disc-shaped member 33 includes acircumferential sidewall 85 which extends from a substantially planar,circular base 87 and terminates in an upper lip or flange 89. Theintersection of flange 89 with sidewall 85 forms a detente 91. One of aplurality of O rings 93 (or other suitable sealing means) is located indetente 91 for creating a seal between disc-shaped member 33 and chamber39.

A second sidewall 97 is located interiorly to the circumferentialsidewall 85 and forms an inner circumference around center 99 ofdisc-shaped member 33. Interior sidewall 97 extends outwardly from base87 and terminates in the form of a seat 37. Seat 37 is thus located on aprojecting portion of the disc surface 77 and has formed therein acavity 101 into which a sealing member 103 is received. Whiledisc-shaped member 33, including seat 37, is preferably made of castmetal, sealing member 103 is preferably formed of polymeric materialwhich has slightly more resilience than cast metal.

A pair of passages 105 extends between opposite surfaces 77 and 79 ofdisc-shaped member 33. Passages 105 extend longitudinally from seat 37and through interior sidewall 97. Longitudinal portions 106 of passages105 proximate to the seat 37 are in communication with cavity 101. Asbest seen in FIGS. 2, 3 and 5 passages 105 have sections 107 of enlargedcross section beginning below cavity 101 (FIG. 5), and such sections 107extend from below cavity 101 to the disc surface 79. Passages 105 thuspermit pressurized gas to flow from one side of the disc-shaped member33 to the other, and the geometry and location of passages 105 allowthem to be formed at the time disc member 33 is cast, rather than bysubsequent and additional machining steps.

Seat 37 has a surface area which is less than that of surface 79 ofdisc-shaped member 33. Accordingly, sufficient pressure in head region81 induces longitudinal movement of seat 37 toward orifice 125.

Sidewalls 85, 97 define an annular trough 95 on disc surface 77. Thesprings 41 are received in the annular trough 95 and extend outwardlyfrom surface 77 at locations which are radially spaced from center 99 ofdisc-shaped member 33. In the embodiment shown, four of the springs 41are formed identically and spaced symmetrically around annular trough95. Thus, each of the springs 41 is angularly spaced from an adjacentone of the springs 41 by an angle of about 90 degrees. Springs 41 arepreferably helical and have longitudinal spring axes indicated at 109.Spring axes 109 are laterally spaced from and substantially parallel tothe longitudinal, central chamber axis 111. In this way, each of thefour springs 41 exert a force substantially in the direction of springaxes 109 against disc-shaped member 33 at four corresponding locationswhich are radially spaced from center 99 of disc-shaped member 33. Assuch, multiple, non-coaxial forces are distributed substantially evenlyover surface 77 during operation of regulator 21 as discussedsubsequently.

One end of springs 41 is biased against disc-shaped member 33 in annulartrough 95. The opposite end of springs 41 is biased against transverseinner surface 65. Transverse inner surface 65 faces or opposes surface77 of disc-shaped member 33. Pins 117 extend outwardly from surface 65toward disc surface 77 and extend at least partly into annular trough95. Springs 41 are longitudinally received by pins 117. The springs 41are thus interposed between the surface 65 and the disc-shaped member33.

Chamber 39 has been provided with means for sealing the chamber 39, hereshown as O-rings 93, thereby creating a zone within chamber 39 which canbe brought above atmospheric pressure when a source of gas is connectedto regulator 21. O-rings 93 are positioned to form seals between thetransverse wall 65 and interior sidewall 97 of disc-shaped member 33,between circumferential sidewall 85 and inner chamber sidewall 119, andbetween endcap 121 and the chamber 33. The sealing provided by O-rings93 creates a pressurized zone 123, which includes a region proximate toterminal end 125 of orifice 31. Pressurized zone 123 is in communicationwith head region 81 through passages 105, and head region 81 thusbecomes a zone above atmospheric pressure as well.

The use and operation of regulator 21 is apparent from the foregoingdescription. When the regulator is not in use, disc-shaped member 33 isbiased by springs 41 into a bottomed-out position against inner chamberwall 67, as shown in FIG. 2. When high pressure gas, such as pressurizedoxygen, is received at a source pressure through orifice 31, zone 123and head region 81 rise above atmospheric pressure, that is, becomepressurized. In response to the pressure of gas received in head region81, disc-shaped member 33 and seat 37 formed therein are urged in anaxial direction toward the terminal end 125 of orifice 31. A sufficientamount of pressure in head region 81 overcomes the bias of the springs41 and, as shown in FIG. 3, causes disc-shaped member 33 to be displaceda predetermined amount toward orifice 31. Increased pressure in headregion 81 urges disc-shaped member 33 closer to terminal end 125. Therear seat 37 is to terminal end 125, the more entry of gas throughterminal end 125 is inhibited.

As pressure in head region 81 decreases, springs 41 urge disc-shapedmember 33 to a position further from orifice end 125 and therebyincrease entry of gas therethrough. In this way, movements ofdisc-shaped member 33 cause regulation of the pressure delivered fromhead region 81 through outlet 32 in communication therewith. Movementsof disc-shaped member 33 thus cause the pressure to be regulated anddelivered at a substantially constant value. The outer limit of movementof seat 37 is when it contacts the terminal end 125, in which positionthe flow of gas through the orifice 31 is stopped until such time as theseat 37 is moved out of contact with the terminal end 125. Duringmovement of disc-shaped member 33, interior sidewall 97 remains incontact with and is guided by, the o-ring 93 between interior sidewall97 and the wall 65 defining the chamber 39.

Although the present invention is useful in a variety of applications,one application receives gas at a source pressure of about 2,000 psi andhas been configured to maintain a delivery pressure of under 100 psi,such as at 50 psi. In such embodiment, the disc-shaped member is movedaxially from its resting position shown in FIG. 2 a distance of about0.028" to maintain a delivery pressure under 100 psi. The amount ofmovement of disc-shaped member 33 may also be affected by gas flowcontrol valves (not shown) which may be attached downstream of thedisc-shaped member 33. Suitable springs for delivery pressures under 100psi have a free length of about 0.31", a cross-sectional outer diameterof about 0.20"; they are made of music wire and have a rate of 110lb/in. Passages 105 are dimensioned to have cross-sectional areas ofabout 0.00192 sq. in.

Various alternatives and variations to the embodiment discussed aboveare also within the scope of the present invention. For example,although regulator 21 uses four of the springs 41, a greater or lessernumber could equally well be used so long as the springs 41 deliverrelatively uniform, forces at multiple, distributed locations spacedlaterally from the longitudinal axis 11. As a further variant, pins 117may be mounted on a separate component within the chamber 39, ratherthan integral with the transverse inner wall 65 as in the illustratedembodiment. Pressure regulator 21 can be equipped with any of a varietyof gas flow control valves so that, in use, any of a variety ofappropriate flow rates may be selected.

Another alternative embodiment of the present invention is shown in FIG.8. The four helical springs 41 have been replaced with a single springwasher 141, also known as a "wave washer" owing to the wave-like formproduced by alternating peaks and valleys. The surface 177 ofdisc-shaped member 133 is formed to be engaged by one side of springwasher 141, while also allowing the other side of spring washer 141 toengage transverse chamber wall 165.

The spring washer has a set of four peaks 143 alternating with a set offour valleys 145. Peaks 143 engage transverse chamber wall 165 whilevalleys 145 engage surface 177 of disc-shaped member 133. As in theprevious embodiments, the spring washer 131 exerts force on disc-shapedmember 133 at multiple, discrete locations 179 which are angularlyseparated from each other about the area of the surface 177.

In addition to the advantages apparent from the foregoing description,the present invention has a length which is sufficiently limited so asnot to extend beyond the cross-sectional footprint of many portable,high-pressure gas cylinders.

As a further advantage, multiple, relatively compact springs aredistributed over the surface of the disc-shaped member 33 at locationswhich are spaced from the center; in this way the necessary resistanceto movement of disc-shaped member 33 in a generally planar, space-savingstructure.

The overall weight of the regulator is reduced by virtue of not only thereduced length but also by the novel positioning of the mounting member43. This reduced weight becomes especially advantageous when theregulator is used in mobile situations or with ambulatory patients.

The invention having been disclosed in connection with the foregoingvariations and examples, additional variations will now be apparent topersons skilled in the art. The invention is not intended to be limitedto the variations specifically described above, and accordingly,reference should be made to the appended claims rather than theforegoing discussion of preferred examples to access the scope of theinvention in which exclusive rights are claimed.

What is claimed is:
 1. A compact gas pressure regulator comprising:ahousing having inlet and outlet ends, a longitudinal axis, and innerwalls defining a chamber, the inner walls including a transverse innerwall located between the outlet end and the chamber; means for sealingthe chamber to create a zone above atmospheric pressure; an orifice inthe housing for receiving gas at a source pressure; an outlet in thehousing for delivering gas at a delivery pressure lower than the sourcepressure; a substantially disc-shaped member movably mounted within thehousing, the disc-shaped member having a center and first and secondopposite surfaces, the first surface having a seat opposing the orifice,the second surface and one of the walls of the chamber defining a headregion in communication with the outlet; and spring means biased againstthe disc-shaped member, the spring means extending outwardly from thefirst surface and exerting force on the disc-shaped member at multiple,discrete locations which are angularly separated from each other aboutthe area of the first surface, the disc-shaped member and the seat beingdisplaced a predetermined amount toward the orifice and against the biasof the spring means in response to the pressure of gas received in thehead region, thereby regulating the delivery pressure; a yoke extendinglongitudinally from the inlet end of the housing, the yoke having armssecured to the housing and extended therefrom, the arms having inner armsurfaces defining a yoke aperture therebetween, the inner arm surfaceslocated a first radial distance from the longitudinal axis; a mountingmember secured to the housing and having sides extending generallyoutwardly from and transversely to the longitudinal axis; and a boreextending through the mounting member adapted to receive a pressuregauge therein, the bore terminating in a bottom which is radially spacedfrom the longitudinal axis by a second radial distance greater than thefirst distance, the bottom of the bore located relative to the chamberso as not to be interposed between the transverse wall of the chamberand the outlet end of the housing.
 2. The regulator of claim 1, whereinthe mounting member is block shaped and secured at one of the arms ofthe yoke.
 3. The regulator of claim 1, wherein the spring meanscomprises a plurality of helical springs having longitudinal springaxes, wherein the chamber has a longitudinal chamber axis, thedisc-shaped member being coaxially aligned with the longitudinal chamberaxis, the spring axes being laterally spaced from and substantiallyparallel to the chamber axis, the disc-shaped member being axiallymoveable within the chamber.
 4. The regulator of claim 1, wherein thespring means comprises a spring washer.
 5. The regulator of claim 1,wherein the disc-shaped member is cast metal and includes a pair ofpassages adjacent to the seat and extending between the oppositesurfaces to allow gas to flow from one side of the disc-shaped member tothe other side.
 6. The regulator of claim 3, comprising four of thesprings spaced symmetrically on the first surface.
 7. The regulator ofclaim 1 for use with a source pressure of about 2000 psi, and whereinthe spring means is selected to resist movement of the seat toward theorifice by an amount sufficient to maintain the delivery pressure underabout 100 psi.
 8. The regulator of claim 1, further comprising means forpermitting flow of gas through said disc-shaped member to the headregion, and wherein the disc-shaped member including the seat is mountedfor movement within the chamber between first and second positions, thefirst position located closer to the orifice than the second position torestrict entry of gas through the orifice, the second position locatedfurther from the orifice than the first position to increase entry ofgas through the orifice.
 9. A compact gas pressure regulator for ahigh-pressure gas cylinder, comprising:a housing having inner wallsdefining a chamber, the chamber having first and second, longitudinallyspaced, inner walls; means for sealing the chamber to create a zoneabove atmospheric pressure; an orifice in the housing for receiving gasat a source pressure; an outlet in the housing for delivering gas at adelivery pressure lower than the source pressure; a yoke extending fromthe housing and defining an aperture adjacent to the orifice forreceiving the high-pressure tank; a T-clamp mounted to the yoke forsecuring the regulator to the tank; a member for mounting a pressuregauge on the housing, the mounting member having a bore therein incommunication with the orifice, the housing having a generally circular,cross-sectional footprint and a length, the mounting member extendingoutwardly from the footprint without substantially increasing the lengthof the housing; a substantially disc-shaped member movably mountedwithin the housing, the disc-shaped member having a center and first andsecond opposite surfaces, the disc-shaped member and the chamber havinga common central axis of symmetry, a plurality of pins extending fromthe first inner wall toward the first surface; a plurality of helicalsprings longitudinally received on the pins and biased against the firstsurface, the first surface having an annular groove, the springs beingreceived in the groove, the pins including the springs received thereonbeing radially spaced from the central axis by a predetermined distanceand positioned relative to each other at regular angular intervals; anda seat on the first surface, the seat positioned to oppose the orifice;the second surface and the second inner wall defining a head region incommunication with the outlet; the disc-shaped member and the seat beingdisplaced a predetermined amount toward the orifice and against the biasof the springs in response to the pressure of gas received in the headregion, thereby regulating the delivery pressure.
 10. The regulator ofclaim 9, wherein the length of the housing is so dimensioned to maintainthe regulator within the cross-sectional footprint of the cylinder whenthe regulator is attached to the high-pressure cylinder.
 11. Theregulator of claim 9 comprising four springs, wherein each of thesprings is angularly spaced from and adjacent space by an angle of about90 degrees.
 12. The regulator of claim 9 wherein the mounting membercomprises a block.
 13. The regulator of claim 9, further comprising apair of passages adjacent to the seat and having openings at theopposite surfaces of the disc-shaped member to allow gas to flow fromone side of the disc-shaped member to the other side, the passagesextending between the opposite surfaces.
 14. A gas delivery apparatuscomprising:a high-pressure gas cylinder having a high pressure outletand a cross-sectional footprint; a gas pressure regulator secured to thecylinder, the regulator comprising:a housing having inlet and outletends, a longitudinal axis, and inner walls defining a chamber, the innerwalls including a transverse inner wall located between the outlet endand the chamber; means for sealing the chamber to create at least onezone above atmospheric pressure; an orifice in the housing for receivinggas at a source pressure; an outlet in the housing for delivering gas ata delivery pressure lower than the source pressure; a substantiallydisc-shaped member movably mounted within the housing, the disc-shapedmember having a center and first and second opposite surfaces, the firstsurface having a seat opposing the orifice, the second surface and oneof the walls of the chamber defining a head region in communication withthe outlet; and spring means biased against the disc-shaped member, thespring means extending outwardly from the first surface and exertingforce on the disc-shaped member at multiple, discrete locations whichare angularly separated from each other about the area of the firstsurface; the disc-shaped member and the seat being displaced apredetermined amount toward the orifice and against the bias of thespring means in response to the pressure of gas received in the headregion, thereby regulating the delivery pressure; a yoke extendinglongitudinally from the inlet end of the housing, the yoke having armssecured to the housing and extending therefrom, the arms having innerarm surfaces defining a yoke aperture therebetween, the inner armsurfaces located a first radial distance from the longitudinal axis; amounting member secured to the housing and having sides extendinggenerally outwardly from and transversely to the longitudinal axis, abore extending through the mounting member adapted to receive a pressuregauge therein, the bore terminating in a bottom which is radially spacedfrom the longitudinal axis by second radial distance greater than thefirst distance, the bottom of the bore located relative to the chamberso as not to be interposed between the transverse wall of the chamberand the outlet end of the housing; the housing having a generallycircular, cross-sectional footprint and a length, the mounting memberextending outwardly from the footprint without substantially increasingthe length of the housing, the housing not extending beyond thefootprint of the cylinder.
 15. A compact gas pressure regulatorcomprising:a housing having inner walls defining a chamber; means forsealing the chamber to create a zone above atmospheric pressure; asubstantially disc-shaped member movably mounted within the chamber, thedisc-shaped member having a center, and first and second oppositesurfaces, the first surface having an inner and outer peripheral wallextending therefrom, the first surface having portions adapted to engagewith means for biasing the disc-shaped member; a seat defined on thefirst surface of the disc-shaped member within the perimeter of theinner peripheral wall, the outer peripheral wall terminating in a lipwhich projects radially outwardly to form a flange at the underside ofthe lip, the flange sized to receive an O-ring thereon; the seat havingportions defining a pair of individual, substantially independentpassages, each passage having a first opening on the first surface and asecond opening on the second surface, the passages extendinglongitudinally between the first and second openings; wherein thepassages have first portions of a first diameter extending from thefirst openings and second portions of a second diameter greater than thefirst diameter extending from the second openings.
 16. The regulator ofclaim 15, wherein the disc-shaped member is made of material selectedfrom the group consisting of cast metal and forged metal.
 17. A compactgas pressure regulator comprising:a housing having inner walls definingchamber; means for sealing the chamber to create a zone aboveatmospheric pressure; a substantially disc-shaped member movably mountedwithin the chamber, the disc-shaped member having a center, and firstand second opposite surfaces, the first surface having an inner andouter peripheral wall extending therefrom, the first surface havingportions adapted to engage with means for biasing the disc-shapedmember; a seat first defined on the surface of the disc-shaped memberwithin the perimeter of the inner peripheral wall, the outer peripheralwall terminating in a lip which projects radially outwardly to form aflange at the underside of the lip, the flange sized to receive anO-ring thereon; the seat having portions defining a pair of passages,each passage having a first opening on the first surface and a secondopening on the second surface, the passages extending longitudinallybetween the first and second openings; wherein the disc-shaped member ismade of material selected from the group consisting of cast metal andforged metal, and wherein the passages have first portions of a firstdiameter extending from the first openings and second portions of asecond diameter greater than the first diameter extending from thesecond openings; wherein the seat comprises a central cavity and asealing member received in the central cavity, the first portions incommunication with the central cavity and adjacent to the sealingmember.
 18. A compact gas pressure regulator comprising:a housing havinginner walls defining a chamber; means for sealing the chamber to createa zone above atmospheric pressure; an orifice in the housing forreceiving gas at a source pressure; an outlet in the housing fordelivering gas at a delivery pressure lower than the source pressure; asubstantially disc-shaped member movably mounted within the housing, thedisc-shaped member having a center and first and second oppositesurfaces, the first surface having a seat opposing the orifice, thesecond surface and one of the walls of the chamber defining a headregion in communication with the outlet; and spring means biased againstthe disc-shaped member, the spring means extending outwardly from thefirst surface and exerting force on the disc-shaped member at multiple,discrete locations which are angularly separated from each other aboutthe area of the first surface. the disc-shaped member and the seat beingdisplaced a predetermined amount toward the orifice and against the biasof the spring means in response to the pressure of gas received in thehead region, thereby regulating the delivery pressure; wherein thespring means comprises a plurality of helical springs havinglongitudinal spring axes, wherein the chamber has a longitudinal chamberaxis, the disc-shaped member being coaxially aligned with thelongitudinal chamber axis, the spring axes being laterally spaced fromand substantially parallel to the chamber axis, the disc-shaped memberbeing axially moveable within the chamber; wherein the inner wallsinclude an inner transverse wall longitudinally spaced from thedisc-shaped member, the transverse wall having at least two pinsextending toward the first surface of the disc-shaped member, thesprings being longitudinally received on the pins and extending betweenthe transverse wall and the disc-shaped member.
 19. A compact gaspressure regulator comprising:a housing having inlet and outlet ends, alongitudinal axis, and inner walls, the inner walls defining a chamber,the inner walls including a transverse inner wall located between theoutlet end and the chamber; a yoke extending longitudinally from theinlet end of the housing, the yoke having arms secured to the housingand extending therefrom, the arms having inner arm surfaces defining ayoke aperture therebetween, the inner arm surfaces located a firstradial distance from the longitudinal axis; a mounting member secured tothe housing and having sides extending generally outwardly from andtransversely to the longitudinal axis, a bore extending through themounting member adapted to receive a pressure gauge therein, the boreterminating in a bottom which is radially spaced from the longitudinalaxis by a second radial distance greater than the first distance, thebottom of the bore located relative to the chamber so as not to beinterposed between the transverse wall of the chamber and the outlet endof the housing.
 20. The regulator of claim 19, wherein the mountingmember is block shaped and secured at one of the arms of the yoke.